Engine for transmitting forces developed therein



|-|. DE WAIDE 2,658,486

ENGINE FOR TRANSMITTING FORCES DEVELOPED THEREIN Nov. 10, 1953 5 Sheets'-Sheet 1 Filed April 23, 194? Inventor Am, D'aWF DE By Httorneys Fig.5

Nqv. 10, 1953 H. DE WAIDE 2,658,486

ENGINE FOR TRANSMITTING FORCES DEVELOPED THEREIN Filed April 25, 1947 5 Sheets-Sheet 2 11/4 IIIIII/ IlIlIlIII/I Inventor Nav. 10, 1953 H. DE WAIDE 2,658,436

ENGINE FOR TRANSMITTING FORCES DEVELOPED THERE IN Filed April 23, 1947 5 SheetsSheei 3 FigJO Inventor F 9 A Ax. 'DEWA\ DE Httorrregs Nov. 10, 1953 H. DE WAlDE 2,658,486

ENGINE FOR TRANSMITTING FORCES DEVELOPED THEREIN Filed April 25, 194'? 5 Sheets-Sheet 4 F1 12 Inventor Hm. DEW ADE Httorne gs Nov. 10, 1953 H. DE WAlDE 2,658,486

ENGINE FOR TRANSMITTING FORCES DEVELOPED THEREIN Filed April 25, 1947 5 Sheets-Sheet 5 hin-III- 599 m 7/11/1114 I "I v I I mull.

Inventor Hbtorrregs Patented Nov. 10, 1953 UNITED STATES FATENT OFFICE ENGINE ron TRANSMITTING FORCES DEVELOPED THEREIN Hal De Waide, Seattle, Wash.

Application April 23, 1947, Serial No. 743,238

Claims.

My invention relates to the art of engines for transmitting forces developed therein. More particularly my invention relates to an engine characterized by the use of liquid as a power transmitting means between a fluid pressure chamber or working chamber and a mechanical, torque delivery or converting means.

My invention will be set forth primarily herein as applied to internal combustion engines, but it is to be understood that it is not to be restricted to any such specific application but extends to all uses where like conditions exist in whole or in part, such as in any engine receiving its fuel or energy through externally developed pressure and running as a motor. Be it particularly noted that where examples are cited and modifications are set forth that the same are given as illustrations and not as limitations unless the context otherwise indicates.

Definite mechanical limitations are present in commonly known as the crank chain linkage,

which linkage provides a fixed geometrical relationship.

My invention relates to a device which uses a liquid in lieu of the conventional rigid connecting rod for th transmission of energy between a, reciprocating piston member and a rotating shaft. In my invention there is suitably connected to the rotating shaft an eccentrically mounted rotating liquid displacement member and mounted in a housing having a plurality of compartments. The operation of said displacement member alternately' impells and retracts the liquid in each partitioned part of the housing. This alternate flow within the compartments produces a reciprocating liquid body, similar to the piston action of a conventional engine.

A primary object of the invention herein set forth is the providing of instrumentalities herein called abutment members to hold off the expansion pressure of the power transmitting liquid as respects a certain circumferential portion of the displacement member and thereby allow and direct the expansion pressure of the power transmitting liquid toselectively act directly'only' upon a certain other portion of the displacement member that is,. that portion where the greatest leverage may be obtained.

In connection with thus providing for greatly increased. efiiciency of this type of an engine, there is involved the relieving of pressure on certain portions of the circumference of the displacement member. Furthermore, the power transmitting liquid, being subject to the heating or the explosive or force producing fluids in the working chamber, become heated and it is a primary purpose of my invention to provide for the continued cooling of the power transmitting liquid.

The providing of an engine employing liquid as the power transmitting means presents at the outset fundamental difiiculties, for example, it may be questioned how is a liquid means having no tensile strength (only compression strength) to be used in a high speed reciprocating engine as the power transmitting means? How, with such a medium, is a predetermined spaced relationship between the power producing fiuid operating in an expansible chamber type of engine to be maintained with respect to its power shaft? How is such a power transmitting liquid to be sealed between its moving members where high velocity wear may be expected? How is balanced volumetric relationship of the power transmitting liquid to be established and maintained in relation to a uniform volume of Working fluid? How is the jetting action of liquids in motion to be controlled? How may an engine b provided which may develop greatly increased torque withoiit conventional torque increasing means, such as conventional transmission means, and this without loss of maximum operating efiiciency? These are only a few of the problems which my invention and discovery has solved.

Furthermore, besides crank-chain linkage limitation, another fundamental difiiculty inherent in internal combustion engines relates to its ability to breathe, that is, getting a suincient quantity of air into a given space for combustion and th elimination therefrom of the exhaust gases. Increasing the valve area when exposed to the high temperature gases of combustion in the conventional type of engine does not solve such air problem because the increased area accelerates or builds up a contra-acting sealing problem, due for one reason to increased warping problems and increased wear due to lubricating d-ifii'culties, to say nothing of involved increased inertia and functional mechanical problems. A fundamental purpose of my discovery or invention is to overcome the difficulties and. limiting restrictions to air flow and velocity of conventional internal combustion engines by providing. a type of engine of my imreiition employing liquid asthe ower transmitting means;- Accordingly my discovery and invention involves providing for proper lubrication and cooling of valve mechanism.

Still furthermore, th engine in common use and of conventional design with its rigid crank chain linkage has certain inherent positive restrictions, such as its space volume requirement for given power production and weight. A fundamental purpose of my discovery and invention is to provide an engine of a design of far greater flexibility as respects this space and weight feature. My invention and discovery permits designing substantially to any desired bore and stroke relationship.

For one example, an engine may be designed having a small bore and an exceptionally long stroke within a very small space and likewise an engine of fairly large bore and very short stroke may be designed for the same small space. So much for the space feature, and now as to the weight feature: In the engine in common use and of conventional design having the rigid crank chain linkage, the stresses in power production are concentrated necessarily upon parts of relatively small area and consequently the said parts are necessarily of relatively heavy construction to absorb the stresses incident to highspeed reciprocation. By providing an engine of my discovery and invention involving the employment of liquid as the power transmitting means, the said stresses may be distributed over i relatively large areas and therefore the parts may be made of much less weight and of much simpler and economical constructionparticularly more compact.

Through the rigid mechanical linkage in the conventional internal combustion engine, the piston is compelled to apply its maximum pressure at the minimum leverage position of the crankshaft and can only apply a reduced pressure to the maximum leverage of the crankshaft when the piston is halfway down in its stroke. At this point of the stroke the pressure above the piston has been greatly reduced through expansion and loss of heat through cylinder walls. Thus, there results a great loss of power and efficiency. In the engine of my invention, the increased leverage of the power transmitting liquid type of engine over that of the conventional crank chain type is still further augmented by the provision of the abutment members of my invention.

Another important advantage of my invention made possible by the use of a liquid power transmitting means, operating in place of conventional rigid connecting rods, is that by immersing all the principal moving parts of the engine in a liquid, which serves both as a coolant and lubricant, the use of non-metallic parts is made feasible, if desired, to substitute them for metallic members. Many such materials are adaptable for usage under this submerged condition, particularly synthetic and plastic moldable materials. Hard phenolics and phenolics with fibrous inclusions are particularly adaptable, as well as organic materials, such as rubber, woods, and flexible synthetics. Phenolics with a cloth filler may be employed in my invention as they are capable of withstanding extreme bearing pressures with only water used as the lubricant.

Various liquids may be employed for the liquid operating as connecting rods, or the power transmitting liquid means. The use of mercury, silicones, tetracresyl silicate (liquid heat), or other high temperature resistant liquids for a liquid piston, or for power transmitting means, are advantageous due to their high boiling points,

which permits in my engine, higher cylinder temperatures with a resulting higher fuel efficiency. In general, the engine of my invention is adaptable to use fuels other than liquid fuels, for example, powdered coal, producer gas such as that made from organic material, coal, straw, and waste wood products. Obviously, the device of my invention is adaptable to the use of fuels Widely differing fundamentally in character.

My invention is particularly adaptable to providing an engine of much more efficient type to operate as, or to do the work of, the conventional diesel type engine.

Objections to diesel engines as heretofore commonly constructed are as follows:

Engines of the diesel type are inemcient because their power is applied through a mechanical linkage which operates angularly thereby forcing the p-istons circumferential surface against the cylinder walls with great force resulting in inefficient sliding friction and great wear. Accordingly, the maximum power at the piston head is only partly available for producing net turning effort. As great pressures are thus constrained by the mechanical linkage and bearings, there is generated a considerable amount of frictional heat which escapes through the cooling system and is thus not available as useful power.

The conventional diesel engine mechanism is formed of parts of great complexity, which of necessity must be accurately machined and fitted. Particularly, accurate finishing is required of crankshafts, bearings and valving means.

The problem of lubricating the diesel engine, as now constructed, requires extensive special provisions. Lubrication requirements along with other limiting features, which characterize the diesel engine of today, renders it necessary to operate it at a maximum of about 200 F. for its coolant.

Throughout the history of diesel engines, engineers have striven to reduce the weight per horse power developed. The considerable weight and space required in relation to the net horse power produced is one reason why the potential field for utility of diesel engines has been restricted to services permitting such weight. In short, the excessive weight, space, and high manufacturing cost per horse power of the conventional diesel engine has definitely restricted its field of application.

The cost of construction of the diesel type of engine is relatively high. The employment of mechanical linkage rigidly limits the minimum size of the moving parts, the angularity of power application to crank leverage, cylinder bore and stroke, and the revolutions per minute. The diesel type of engine to be fully reversible requires additional complexity of mechanism.

A primary object of my invention is to provide a power developing or transmitting device operating on the diesel cycle which overcomes and solves the deficiencies above noted, and particularly to produce a mechanism characterized by the following features: Its increased efiiciency; Its simplicity-being of a type by which its parts or for most part may be formed by die stamping; Employment ofv phenolic plates in place of metal; Welding assembly; compactness; and Nonuse of special lubricating oils; Operating at temperatures up to twice as high as presently employed; Greatly increased horse power per unit weight; and greatly increased effectiveness of the fuel consumed thereby permitting an increase of the available power.

A further advantage is that liquids are characterized by being substantially non-compressible yet highly mobile. As a power transmitting means such liquids do not require additional lubrication and may be subject directly to cooling action.

Features which characterize my invention are:

(l) Balanced volumetric relationship;

It is fundamentally important to locate the axis of rotation of the power transmitting liquid rotatable displacement member with respect to the partitioning means, such that the displacement member will displace equal volumes of the power transmitting liquid in each partitioned space or chamber, thereby insuring equal reciprocating piston-like bodies in the working chambers (i. e., the chamber corresponding to the cylinder in the conventional engine). Also, such balanced relationship provides equal working fluid (i. e., the force developing or expandible source of power) volumetric working spaces (corresponding to the compression spaces in the conventional internal combustion engine).

(2) Predetermined operative spaced relationship between the acting surface of the reciprocating body (liquid or interposing member piston or interposed buoyant leveling body) as respects the working fluid and the rotating displacement member.

A primary purpose of my invention is to employ the power transmitting liquid not only as a power transmitting liquid but also as a liquid sealing means to maintain a definite predetermined relationship between the top of the liquid column and the eccentric displacement member. This is important in order to have a definite fluid volume for the working chamber or cylinder. While on one hand it is important to have a definite fluid volume in the working cylinder at each stroke of the engine, it is also equally necessary to have the relationship of the top of the liquid column and the displacement member uniformly maintained. The power transmitting liquid, it will be understood, operates as a flexible linkage means in connecting the forces developed in the fluid chamber to the eccentrically mounted displacement member to rotate the shaft. Where the periodic force-developing fluid reacts directly again the surface of the piston-like column of liquid we have the simplest form of my invention as. respects such elements.

In connection with the above are the means of maintaining the power transmitting liquid at a predetermined level by means of the use of a conventional surge chamber and an adjustable mechanical liquid displacing means operating upon the power transmitting liquid. This is one of the means for maintaining the uniform spaced relationship of the top of the liquid column and the displacement member. Any employment of a conventional sliding seal as a packing manifestly clearly involves wear and when it is remembered that the piston must reciprocate very rapidly, it, is evident that very shortly there will develop such wear, as to permit. leakage of air or fluid, particularly when there is a minus pressure on the underside of the piston. By providing a trapped interposed liquid seal such wear and leakage is prevented.

(3) Cylindrical Ring and sealing of power transmitting liquids in compartments;

To use a liquid as a power transmitting means, obviously, involves its confinement to definite channels to render available its incompressible characteristic. To the degree that the structure 6 of the engine permits leakage by so much is the efliciency of the engine lessened. Thus, the matter of proper sealing is fundamentally requisite in establishing and maintaining the predetermined spaced relationship set forth above.

A primary purpose of my invention is to provide sealing means so that pressures developed in a compartment are efficiently employed through shaft rotation. Accordingly, my invention and discovery involves various means of providing insured sealing of the power transmitting liquid, for example, (a) movable partitioning members including within their faces rockable surface contacting sealing elements; (2)) annular idling member (herein referred to as cylindrical ring) to alter relative pressure and velocity relationship, thereby achieving high sealing and low wearing factors; (0) means providing for augmenting and maintaining pressures upon the interlocked sealing element; (01) means providing for trapped interposed liquid sealing against fluid leakage which would destroy predetermined spaced relationship between the parts as set forth above; (e) means providing turbulence by establishing a counter flow of the liquid or interruptin the continuous flow, thus further reducing the efficiency of flow through a given orifice so that the leakage is further reduced; (f) means creating multiple orifices to further reduce the leakage in combination with inducing turbulence; and (9) means for minimizing the areas subject to being acted upon by unseating pressures acting upon partitioning members to disengage them from their sealing contact with the displacement member.

(4). Abutment;

The purpose of the abutment member of my invention is to selectively guide and direct the pressure developed in a compartment to that part of the displacement member desired, that is, to that part of the displacement member whereby the maximum rotative effort may be obtained from the power transmitting liquid at its maximum pressure, and also for applying pressure upona selected portion of the circumference of the displacement member, that is, under a selected range of leverage of said displacement member. This provides also a new method of reciprocating power application to a rotating shaft by applying maximum pressures to maximum rotating leverage differentiating thereby from the conventional crank chain rigid connection rod linkage which applies maximum pressures at minimum rotative leverage. It will be remembered that the rigid crank linkage applies the maximum pressures very close to dead center. This abutment arrangement permits application of pressures to rotating efiort at any desired degree between the maximum and the minimum rotative leverage thereby being in direct contrast to the inflexible conventional crank chain linkage which operates in a sequence of rigid relationship.

(5) Cooling means;

The academic rule is that the hotter the cylinders are operated, the more eflicient is the internal combustion engine. However, there are certain practical limits. The cylinder cannot be allowed to become too hot because then pre-ignition occurs in both diesel as well as in the Otto cycle.

One of the objects of my invention herein is to provide a means where the combustion can take place at a higher temperature than is now commonly employed. In accomplishing this, I

provide means for the removal of excessive heat accumulation by internal cooling, as distinguished from external cooling, as is conventionally employed. This is done through the medium of the power transmitting liquid.

(6) Efiicient scavenging of gases or fluids to be exhausted;

One of the basic limitations of an expansible chamber engine is the providing for rapid scavenging of the fluids to be exhausted. A primary object of my invention and discovery is the overcoming of this limitation and providing for increased efiiciency relating thereto.

('7) Flexible design dimensions permitting fitting and adapting to space requirements;

A feature characterizing my invention in using power transmitting liquid as a flexible connecting rod, is that it may have relatively great horse power in relatively small space as compared to conventional rigid connecting rod engines. This compactness is due to the engine of my invention providing for the use of a short liquid flexible member as a substitute for conventional rigid connecting rod and at the same time providing for avoiding the high side thrust, high wear and high friction which is inherent with the use of a short rigid connecting rod in the conventional engine. On the other hand, when the conventional engine employs a long rigid connecting rod to reduce said thrust, wear and friction, its resulting space requirements are greatly increased and thus results a large bulky engine of excessive weight. However, when desired, or conditions require, the engine of my invention provides for a long flexible liquid connecting member, as when the displacement member of the engine is submerged in water in a well or mine shaft and the working cylinders are placed above ground.

(8) Widely spaced working cylinders from rotatable displacement member;

(9) Economical construction and minimum machining;

A primary object of my invention is to provide an engine of economical construction by reason of the fact that it may be integrally formed of cast parts, which require a minimum of machining for precision fitting.

Other characterizing features are inherent in the various structures disclosed.

By working cylinder is meant herein the forms of means as follows: (a) Cylinder and liqnid piston as illustrated in Fig. 1 and Fig. 2; Cylinder with piston member (1) interposed between the power transmitting liquid and the explosive fluid or (2) in case of pump device, in-

terposed between the power transmitting liquid and the material, gaseous or liquid, being acted upon, as shown in Fig. 9.

The above mentioned general objects of my invention, together with others inherent in the same, are attained by the mechanism illustrated in the following drawings, the same being preferred exemplary forms of my invention:

Figure 1 is a cross sectional view of a preferred form of engine embodying my invention;

Fig. 1a is a fragmentary sectional view showing a plurality of idly mounted cylindrical rings mounted on displacement member to provide improved velocity-pressure relationship and to assist sealing orifice effect;

Fig. 2 is a longitudinal view in elevation of the same;

Fig. 3 is a fragmentary sectional view showing the rotor member advanced over the position shown in Figure 1;

Fig. 4 is a diagrammatic sketch showing application of forces to the lever arm of the rotating displacement member;

Fig. 4a is a fragmentary view of the rotating displacement member with parts broken away to show side sealing means;

Fig. 4b is a fragmentary view showing a detail in the form of a modified slide block means;

Fig. 4c is a view in perspective of a partitioning member having turbulent sealing grooves;

Fig. 5 is a cross sectional view of another modified form of my invention showing valve ports in the side or end members of an engine of my invention;

Fig. 6 is a plan view of the modified form shown in Fig. 5;

Fig. 7 is a detailed sectional view on dotted line l'i of Fig. 5;

Fig. 8 is a view in perspective of the valve operating mechanism and ports with parts broken away of the modified form shown in Fig. 5;

Fig. 9 is a cross sectional view of still another modified form of my invention showing fixed forms of abutment members;

Fig. 10 is a longitudinal View of the modified form shown in Fig. 9 with parts broken away;

Fig. 11 is a diagrammatic sketch showing the application of forces to the lever arm of a rotating displacement member of my invention through the use of the abutment members;

Fig. 12 is a vertical sectional view of still a further modified form of an engine embodying my invention showing movable abutment members and arcuately moving partitioning members coactingly connected together with resilient means and with other improved valving features;

Fig. 12a is an enlarged detail of the piston structure and associated parts of Fig. 12;

Fig. 13 is a longitudinal view of the modified form shown in Fig. 12 with parts broken away;

Fig. 14 is a plan view of the modified form shown in Fig. 12;

Fig. 15 is a detailed view of a valving and fuel admitting means of modified form shown in Fig. 12; and

Fig. 16 is a View in longitudinal section illustrating valve operating means of the modified form shown in Fig. 12

Only preferred forms of my invention are set forth. Of these the one disclosed in Fig. 12 and connected figures constitutes a particularly preferred form. It is to be remembered that any particular form or combination of forms of my invention may be employed to meet particular operating requirements.

The more simple of the preferred forms for a wide general use of my invention (Figs. 1 and 2) has housing I90, with driving shaft iill preferably centrally located with respect to the housing I00 and partitioning means E94 and I05 to provide balanced operation. On shaft I0! is fixedly and eccentrically mounted a rotatable displacement member I02 of cylindrical form. Upon displacement member N32 is freely mounted a ring member I03 of cylindrical form which in operation rotates with slippage with respect to displacement member H12 in order to provide a rate of sealing surface rotation less than that of the displacement member 102, thereby minimizi g wear of contacting surfaces. Reciprocal sliding partitioning members I64 (upper) and (lower) are preferably located in the vertical plane through the axis of the shaft I 9| or axis of rotation, each bearing upon ring member I03 through rockable upper and lower sealing memhere I06 and I51 respectively. Upper and lower guide blocks I38 and I39 respectively mount in recesses I Hi and I I I the sliding partitioning members I04 and IE5. Rockable sealing members H2 may be mounted in upper guide I98 to bear upon upper partitioning member I04 and rockable sealing member IIfi may be carried by partitioning member IE4 to bear against the sides of recess IIB. Lower guide block I39 may have rockable sealing members II4 bearing against lower partitioning member I05. Said member Hi5 may also have rockable sealing members H5 mounted therein to bear against the walls of recess III. Recess II!) has opening H3 which is connected by tube I I1 to opening I I8 in recess III.

Guide block I08 has arm I It. Guide block N33 has arm I23. Arms IIS and I23 serve as partial partitions. They also serve as pivotal bearings for movable abutments I2I and I22 respectively and cause leading end portions I 25 and I25 thereof to bear upon rin I03 to form a liquid tight seal therewith. The following end portions I21 and I28 of abutments I2I and I22 respectively are provided with valve seats I29 and I35, Which seat upon valve seats I3! and I32 carried respectively on guide blocks Hi8 and I39, forming chambers I33 and I34. Openings I35 and I36 in said chambers I33 and I34 respectively are connected by tube I31.

The housing I!!!) with its end walls I38 and I39 form a liquid confining chamber composed of two compartments I45 and MI, preferably equal, which are provided with liquid I42. This liquid is reciprocated and caused to function piston-like and also as a power transmitting means, thus taking the place of conventional rigid connecting rods. The housing I04 has extensions I43 and I44 forming fluid expansion chambers I45 and I46. Air inlet tubes I41 and I48 located respectively in chambers I45 and I46, connect with air supply tubes I49 and Isl} respectively and these tubes connect with air supply tube I5I which is connected to a conventional air compressing mechanism I52. Air inlet tubes I41 and I48 have conventional streamlined poppet valve members I 53' and I54 respectively. Valve members I53 and I54 have springs 55 and I54 respectively and are operated by push bars I51 and I58. Chambers I45 and I45 communicate with exhaust outlets I59 and IE respectively through conventional poppet valves I! and E52, operated by push bar I57, respectively as respects chamber I 45 and valves I 63 and IE4, operated by push bar I53, as respects chamber I46. Each of these valves has springs IE5 of identical construction. Push bars I51 and ibii are operated by rocker arms I66 and I61 respectively which arms in turn are operated by push rods I68 and IE9. These push rods I58 and I69 are operated by cams I?!) and I'll mounted on shaft iIlI.

Conventional fuel injectors I12 and I13 are inserted in chambers I45 and I46 respectively and are supplied with fuel by conventional fuel pumps which are not shown. Fly-wheel I14 is mounted on shaft IEBI. Partitioning members I54 and are forced by liquid I42 under pressure to bear tightly against ring IE3 to seal off th liquid in one compartment from that in the other. Recess III communicates with compartments I48 and MI by means of check valves I15 and 15 respectively which are adapted to supply liquid under pressure from the liquid in that compartment I43 or I4I whichever is under the highest pressure. Liquid level regulator I11, operatively disposed in id housing extension I18, regulates the liquid level in expansion chambers I45 and I46.

In Fig. 2 packings I83 and IE4 are mounted in end members I38 and I39, about shaft IIJI to prevent leakage of liquid I42 from housing IIIII. Displacement member I02 and ring member I03 are in close sealing contact with end walls I38 and I39. Flywheel I14 is shown mounted on shaft IIJI.

The mode of operation of said engine of my invention is as follows:

The stage of operation illustrated in Figure l is that combustion and expansion has taken place in chamber I45, valve I53 has opened and is admitting scavenging air from air compressor I52. Thus, exhaust gases are being forced past exhaust valves HM and I62 into exhaust outlet I59. The expansion in chamber I45 has placed liquid I42 in compartment i lIJ under pressure and thereby forced eccentrically mounted displacement member N32 to rotate to position shown. This actuating of member I32 has displaced liquid I42 in compartment I4I forcing it to rise in chamber I46 thereby compressing the fluid therein and raising its temperature to the ignition point of th fuel. The fuel at that point is injected into chamber I46 through fuel injector I13. It will be understood that just prior to the raising of the liquid I42 in chamber I46, air intake valve I54 has been closed by valve spring I53. Likewise exhaust valves I53 and I64 have been closed by associated springs I65.

Upon ignition and expansion taking place against liquid I42 in compartment I4I, the liquid is placed under pressure. This liquid I42 under pressure is directed against rotatable displacement member IE2 at its point of greatest leverage by abutment I2I which causes the displacement member Hi2 to rotate and turn driving shaft IEII.

As expansion forces cause displacement member Hi2 (note position of its as and y axis) to turn and move displacingly into compartment I46, see Fig. 3, orbit I82 is shown at dotted line, the liquid in chamber I45 drops to the level at which the liquid is illustrated in chamber I45 due to the liquid occupying the space vacated by the eccentric portion of the displacement member I32, Thus a complete cycle of the engine operating as a two-cycle engine has been set forth and it is apparent that the operation of the parts in compartments I49 and MI are the same at successive or alternate stages.

By having tube I Ii connecting recesses I I0 and III is provided hydraulic means for sealingly pressing partition members I04 and I with equal pressures against ring Iil3providing 'a positive mechanical sealing contact. The rockable members I93 and II)? are adapted to conform to the curved surface of ring 33 at all positions of its rotation. The rockable sealing members I I2 and I I4 together with rockable sealing members H3 and H5 also insure effective sealing. Manifestly, as one partition member is moved displacing into its recess, the reciprocal liquid is forced through tube II? to the opposite partitioning member to maintain it in positive sealing relation. Additional booster pressure is applied to this reciprocal liquid through check valves I15 and I18 from that particular compartment I43 or I4I having the greatest pressure. To minimize localized friction wear due to high velocity and high pressures on small area, ring I03 having a Wide bearing area on displacement member I32 and a slower rotational rubbin speed is interposed between the high velocity speed of the displacement member I02 and the localized pressure area of the rockable member mounted within the end portion of the sliding partitioning members I04 and I05.

The said relatively slower speed or rotation of the ring member I03 has also the important beneficial function of producing turbulence in the liquid and establishing additional restrictive orifices as respects the end walls I38 and I39 and rotative members (ring I03 and displacement member I 02) in assisting efficient sealing relation between the compartments I40 and MI. The power transmitting liquid I42 tends to escape from the compartment under pressure to the other compartment having less pressure through the orifice-like opening represented by the necessary running clearance between the end walls I33 and I39 on the one hand and the rotating displacement member I02 with its ring I03. By providing difference of rotational speeds for the idly mounted ring I03 and the displacement member E02, my invention creates a turbulent condition in the liquid thereby utilizing the liquid itself to resist passing through the clearance orifice and thereby assists effective sealing between compartments as respects the end portions of the displacement member. In addition, the ring I03 in conjunction with displacement member I02 creates a plurality of restrictive orifices across the line of liquid leakage so that opposition to leakage is greatly augmented. The restrictive orifice areas are established in the fol lowing order: First, the liquid must pass from the compartment under pressure between the ring I03 and the end wall affected; second, between the end of the displacement member I02 and the end wall; and third, between the ring I03 and the end wall affected to reach the compartment having lesser pressure.

Let it be particularly noted that by providing the rockable sealing members I06 and H11 extending substantially fully across and only across the full face of the end portions of partitioning members I and I05, it is manifest that a novel effective sealed partitioning is provided. By having the rockable sealing members I06 and I 0'! so extending fully across and only across the face of the end portions, prevents substantially any surfaces being exposed to high pressures periodically developed in compartment I40 and MI r from acting against such end portions to unseat them, that is, to operate to such extent to nullify the sealing. The efficiency of the machine depends in large measure upon preventing leakage of the power transmitting liquid from one compartment to the other.

The functioning of the abutments I2I and I22 is as follows:

The resilient means I23 caused the leading edge of abutment i2I to extend into the path of rotation of displacement member I02 and as member I02 continued its rotation abutment I2I pivoted on arm H9, thereby causing the valve seat I29 on the following edge to become unseated as respects its seat I3 I. Thus, trapped power transmitting liquid I02 between ring I03 and abutment I2! is permitted to escape into chamber I33 and thence through opening I35 into the tube I3'I. This liquid under pressure then enters chamber I3 through opening I which forces abutment I22 against resilient means I24 into unseated position as respects seats I 30 and I32, thus permitting the liquid under pressure in tube II 'I to escape into compartment I40 which at this stage is an area of lesser pressure as it is not under expansion or compression pressure. When the trapped liquid ceases flowing from chamber I33, resilient mean I24 forces abutment I22 to rotate, thereby bringing valve seats I30 and I32 into closed position (see Fig. 3) which, acting as a check valve, prevents escape of liquid I42 from compartment I90 to MI. In this wise, opposing pressure to the rotation of the displacement member I02 is removed by its transfer to the area of lesser pressure, namely, to compartment I40. Thus the function of the abutment I2I is manifest as a means of protecting or holding off the expansion pressure of liquid I42 in compartment I AI as respects the upper circumferential portion of the displacement member I02 and allows the expansion pressure of liquid I 52 in compartment I4I to act directly only upon the lower portion of the displacement member I 02, i. e., at its greatest leverage. As displacement member I02 continues to rotate, resilient means I23 and the liquid under compression (as distinguished from expansion) pressure causes the leading edge of abutment I2I to bear tightly and liquid sealingly against ring I03.

This situation is diagrammatically represented in Fig. 4 which further illustrates how the expansion force is applied to the longest lever arm (that part of the axis X between the center of driving shaft IOI and the periphery of displacement member I02). The long axis of the eccentric displacement member I02 is identified herein as X, while the short axis at right angles to X, as Y. In the drawing, Fig. 4, the net driving force on the longest lever arm is represented by the large arrows I19. The pressure forces on this longest lever arm necessary to balance or offset the forces resisting turning effort are shown by small arrows Ithe resisting forces being identified by small arrows I8I. Thus, the great power advantage gained through the providing of abutments I2I and I22 is apparent-At being understood that abutment I22 operates in a manner paralleling that of abutment I2I. But the abutments I2I and I22 function to hold off the counter rotation forces and direct the application of maximum expansion forces against the greatest available leverage of the displacement member I02 and thereby provides a pronounced mechanical efficiency.

Figure 1a represents a modified form of my invention where a plurality of cylindrical rings are employed. On shaft I95 is fixedly mounted a displacement member I9I and on this displacement member are idly and fioatingly mounted cylindrical ring members I88, I 89, and I90. The cylindrical ring I88 contacts the partitioning member I92 through rotatable block member I90-the partitioning member I92 is slidably mounted in guides I93.

The mode of operation of this plurality of cylindrical members I 88, I89, and I90 is: Each multiplies the action of the single cylindrical ring hereinabove set forth and has the added action of providing for inducing liquid turbulence in sealing.

In Fig. 4a, sealing rings 290 and 29I respectively extend into recesses 292 and 293 in rotatable displacement member 294 and ring member 295 of cylindrical form. Passageways 296 and 29'! permit liquid pressure to engage and press outwardly sealing rings 290 and 29I. This construction reduces leakage. In Fig. 4b a liquid sealing ring 298 in a displacement member 299 is pressed outwardly by resilient means 300 which might be of rubber. Be it noted that in both the forms shown in Fig. 4a and Fig. 4b resilient means are provided for urging outwardly the sealing rings 230 and 29!, and .298 respectivelyin Fig. 4a liquid alternately under pressure and in Fig. 4b a resilient means in the form of a spring 303. In 40, the modified form of partitioning member 333 is provided with recesses 304 positioned across the direction of leakage flow as an impediment and to create a turbulent liquid condition for reducing to a minimum the leakage fiow.

In the modified form of my invention illustrated in Figs. 5, 6, 7 and 8', a two-working cylinder engine of my invention operating two cycle is shown having valve ports in the side or end members of the housing and arcuately movable abutment members described as follows: This form of my invention has housing 320 and end or side walls 342 and 343 with driving shaft 32! preferably centrally loce ted with respect to the housing 326. On shaft 32! is fixedly and eccentrically mounted a rotatable displacement member 322 of cylindrical form. Upon displacement member 322 is freely mounted a ring member 323 of cylindrical form which in operation rotates with slippage with respect to displacement member 322. Reciprocal sliding partitioning members 324 and 325 are preferably located in the vertical plane through the axis of the shaft 32! or axis of rotation, each held in sealing relation with the ring member 323 by resilient members 326 and 321 respectively. Upper and lower guide blocks 323 and 329 respectively mount in recesses 333 and 33! the sliding partitioning members 324 and 325, said recesses having openings 332 and 333 connected by tube 334. Likewise said guide blocks 323 and 329 pivotally mount abutments 335 and 333 in bearings 331 and 338. Said abutments have rockable sealing members 339 and 340 and preferably end sealing members of the character shown in Fig. 4a, or 4b. Partitioning members 324 and 325 and ring 323 divide the chamber formed by the housing 323 into two compartments 341 and 348. Abutment 335 has valve operating extension 34!.

This modified form of my invention is characterized by having valving means in the form of a disk 344 with air inlet ports 345 and exhaust ports 343 in compartment 341, while the disk 344 also has air inlet ports 349 and exhaust ports 35!) in compartment 343. This disk 344' may be oscillatingly mounted on shaft 32! and against end wall 343. In the end or side wall 343 are corresponding and registering ports as follows: In compartment 341 are air intake ports 35! and exhaust ports 352 and likewise in compartment 343 are air intake ports 353 and exhaust ports 354. Be it noted that the exhaust valving means may be in the end wall opposite to that in which the air intake ports are located if uniflow scavenging is desired. Disk 344' has valve disk extensions 355 and 351 serving as mountings for springs 353 and 359. Housing 320 has shelf extensions 363 and 3M which also serve as mountings for said springs 358 and 359. Disk 344 has slots 332 and 363 in which stop pins 364 and 355 extend, said pins being fixedly mounted in end wall 343. End wall 343 also has rocker pin 333 extending through disk slot 331, which pin 356 mounts rocker arm 353. End wall 343 has ports 363 and 310 connected by tube 31!. In disk 344 are slots 312 and 313 registering with ports 339 and 313. Air intake manifold 314 communicates with air intake ports 35! and 353 in the end wall 343.

Exhaust manifolds 315 and 316 connect 14 with exhaust ports 352 and 354 in end wall 343. Fuel injectors 311 and 318 are located respectively in the upper part of compartments 341 and 343.

The general mode of operation of this modified form of my invention is similar to that set forth for the form shown in Figure 1 except as to the valving means which operates as follows: As shown in Fig. 5 the air in compartment 348 is being compressed by the liquid 319 being displaced by the rotating of the displacement member 322. By such rotation, the abutment 335 has been caused to move arcuately thereby causing valve operating extension 34! to move upwardly and engage extension 351 which rotates valve disk 344 to bring into open port registration, air inlet ports 345 and exhaust port 348 in the disk 344 by causing them to register with air inlet port 35! and exhaust ports 352 respectively in end wall 343. Thus fresh air enters compartment 341 and exhaust scavenging takes place. At the same time, in compartment 343 valve ports are continued in closed or nonregistering position.

Upon displacement member 322 continuing to rotate, spring 353 and pressure of liquid moves abutments 335 downward whereupon spring 359 rotates clockwise disk 344 until pin 365 through opening 33! in extension 351 engages the spring 359 whereupon rotation ceases, leaving all valve disk ports closed in both compartments. Be it noted that the space between the ports in each compartment and in end wall 343 is double the width of a port Opening so that the valve disk may angularly oscillate to move through three positions, one for open registration and two positions for closed to alternately open and close ports to scavenge the cylinder of exhaust gases. Thus all ports are closed when firing and compressing the charge.

Upon continued rotation of displacement mem-- ber 322 abutment 336 moves outwardly and engages rocker arm 368 which causes valve disk 344 to rotate clockwise to open ports in comp-artment 348, spring 358 returns disk 344 to closed port condition as rotation of displacement member 322 continues. Extension 356 has opening 380 to pass pin 364 precisely as described above for spring 351. Thus a cycle of operation of the valve means has been set forth.

In the above both inlet and exhaust ports are located in a disk at one end of the housing. Cbviously, to provide unidirectional scavenging, the inlet port could be in a disk at one end and the exhaust port in a disk at the other end of the liquid chamber-each disk being of identical construction shown and described above except each disk would have only one type of port.

The modified form shown in Figs. 9, 10 and 11 of the device embodying my invention is characterized by having a fixed form of abutment, and having moving pistons in the working cylinders which are actuated by the liquid member functioning as a flexible power transmitting means in lieu of the conventional mechanical rigid or rod linkage, i. e., crank chain linkage.

A housing 393 with end walls 33! and 332 has a driving shaft 333 rotatably mounted therein. A rotatable displacement member 334 may be key mounted on said shaft 393. A ring member 395 of cylindrical form is idly mounted upon said displacement member 334 as hereinabove explained. Sliding partitioning sealing members 396 and 391 are disposed in a plane through the center of said shaft 393, or axis of rotation.

These sealing members may be provided with rockable sealing members 398 and 399 respectively bearing upon ring 395. Said sliding partitioning sealing members 396 and 391 may be also provided with laterally rockable sealing members 400 and 40| respectively, bearing on guide blocks 402 and 493 formed integrally with the housing 390. Said guide blocks also may be provided with rockable members 404 and 405. Slidin partitioning sealing members 396 and 391 are mounted in recesses 406 and 401 respectively in guide blocks 492 and 403, and said recesses also have openings 408 and 409 respectively. A tube 4|0 connects opening 408 with liquid control box 4| I having upper and lower chambers M2 and 4| 3 separated by a partition 4|4 having valves M5 and M6. Lower chamber 4|3 has partition 4|1 dividing lower chamber 4| 3 into compartments M8 and M9. Tube 420 connects liquid control box 4|| with opening 499.

Displacement member 394 with partitioning members 396 and 391 divide the liquid confining chamber in housing 390 into compartments 42| and 422 to confine liquid 423. Tube 424 connects compartment 422 to compartment 4| 8 of control box 4. Tube 425 connects compartment 42| with compartment 4|9 of liquid control box 4| Fixedly mounted abutment 426 mounted on guide block 402 and housing 390 is operatively disposed with respect to the rotatable displacement member 394 having a concave face 421 lying adjacent the outer orbit of the displacement member 394 and its ring 395. Abutment member 426 is hollow to provide trapped liquid receiving chamber 428. In face 421 is spring operated valve means 429.

Diametrically opposite to fixed abutment member 426 is fixed abutment 430 mounted on housing 390 and guide block 403 similar in construction and operation to member 420. That is, it has concave face 43| and trapped liquid chamber 432,-face 43| having spring operated valve means 433. Valve means 429 and 433 are positively operated by cam 434 through push rods 435 and 436 connected to rocker arms 431 and 438 which respectively engage valve means 429 and 433.

Compartment 42| has working fin radiating cylinder 439, i. e., explosion or expansion chamber with a piston 440 characterized by novel features of my invention as follows: The underside of said piston is formed with a depending wall 44| which maintains close floating contact with liquid 423 as it provides a buoyant chamber 442 between wall MI and the piston head 443 which has the deflecting body 444 adapted to deflect scavenging air to the upper portion of the cylinder 439 to effect uniform scavenging of exhaust gases. Piston 440 is also characterized by having a continuous dependent skirt 460. This piston 440 has guide rod 445 slidably mounted in bracket 446 carried by housing 390 in order to prevent rotation of piston 440 to maintain deflecting body 444 in registering relationship with air intake ports 441 and exhaust ports 448. Cylinder 439 has a fuel injector 449 which is supplied by conventional fuel pump not shown.

Compartment 422 has air compressing cylinder 450 with floating air compressing sealing ring carrying piston 45L Cylinder head 452 has conventional spring operated valve means 453 and 454. Valve means 453 admits air from intake pipe 455 and valve means 454 admits air to air storage chamber 456 formed between wall 451 and housing 390. Air storage chamber 456 communicates with working cylinder 439 through air intake port 441. Exhaust port 448 in cylinder 439 opens into exhaust pipe 458.

The mode of operation of said form of my invention is as follows: Piston 440, Fig. 9, is shown at bottom of its stroke with scavenging taking place. Its power stroke has rotated the displacement member 394 to its minimum displacement position with respect to compartment 423 and to its maximum displacement position in compartment 422, and which has caused liquid 423 in compartment 422 to force piston 45| to its upper limit of travel. This in turn has compressed the air in cylinder 450 and caused said air to open and flow through valve 454 into storage chamber 456 during the period of the rise of piston 45|, so that it becomes available to flow under pressure through port 441 after the latter is opened by being uncovered by the descent of piston 440 in cylinder 439. As fly-wheel 459 revolves it maintains continued rotation of displacement member 394, thereby forcibly expelling liquid trapped in chamber 400 formed between concave face 421, ring 395, and partitioning member 396, through valve 429 which has been opened by cam 434 and associated linkage. Thus, the liquid 423 passes into chamber 428, compressing the air contained therein. This compressed air at a later stage expels the liquid 423 from said chamber 428 when displacement member 394 and its associated ring 395 has rotated to a position which allows valve 429 to open by said air pressure. The same operation takes place as respects chamber 42| and its associated chamber 46| formed at a later stage between displacement member 394, concave face 43 and partitioning member 391, when displacement member 394 rotates to a position indicated by dotted line 462.

In the event that there is leakage of liquid 423 past rockable sealing members 402, 403, 404 and 405, liquid 423 is initially supplied to housing 390 and control box 4 and the latters associated tubes. When compartment 42| is under maximum pressure then this pressure forces liquid 423 through tube 425 into liquid control box 4| thence past valve 4|5 into chamber 4|2 thus placing liquid in tubes M0 and 420 and recesses 406 and 401 under augmented pressure which in turn forces partitioning members 395 and 391 into tightly sealing relation with respect to ring 395. Likewise when the liquid 423 in compartment 422 is at maximum pressure, the same action as just described takes place for compartment 42|. In this case, the pressure is communicated through tube 424 to liquid control box 4| thence through valve 4l6 into chamber 4|2. Thus, a cycle of operation is completed.

In Fig. 11 the application of potential or available power is diagrammatically illustrated with respect to the angular position of the displacement member 394 at 0, 45, and when abutment means are provided in conjunction with the use of liquid functioning as a flexible power transmitting means between the working cylinder and the driving shaft. 0 position is that position of the piston at its maximum upward travel due to the maximum displacement position of the rotatable displacement member. The other positions follow in order as rotation of the displacement member progresses. At all positions, the available power is represented by small arrows 463 and the amount of transmitted power is shown by long arrows 464. It will be noted in positions 0, 45 and 90 that the amount of transmitted power is equal to the amount of available power. It will be understood that the available power decreases and has the progressively reduced number of small arrows shown above the piston as the piston descends due to expansion and loss of heat. At said positions of 45 and 90 the abutment is operative in directing the application of the transmitted force to the displacement member 394. In positions 135 and 180, the abutments are not operative and the transmitted power is lessened with respect to the available power. The dotted line 455 indicates that no power is being transmitted.

Figs. 12, 8, 12a, 13, l4, l and 16 show a further modified form of an engine embodying my invention showing movable abutment members and arcuately moving partitioning members coactingly connected with resilient means together with oher improved valving features.

In housing 549, a driving shaft 541, preferably centrally located with respect to the housing 549, has eccentrically mounted a' rotatable displacement member 542, on which is idly mouned a ring member 543 of cylindrical form, which in operation rotates with slippage with respect to displacement member 542. Arcuately movable partitioning members 544 and 545 are pivotally mounted on shafts 546 and 541 respectively and sealingly bear on housing 540. Said shafts extend through end wall 549 with hearing mountings as respects one end thereof, while the other end has a closed end bearing in wall 549 (see Fig. 13). Said partitioning members 544 and 545 have rockable sealing members 559 and 55l which sealingly bear upon ring 543. On shafts 545 and 541 are mounted lever arms 552 and 553, respectively, the outer ends of which are operatively connected to a joining rod 554. On this rod 554 is mounted on one end portion a resilient member 555 which bears against the outer end portion of lever arm 552, through which said rod slidingly passes in hole 555.

Partitioning members 544 and 545 together with displacement member 542 with its ring 545 divide the chamber formed by housing 549 into two comparments 551 and 558.

Arcuately moving abutments 559 and 559, having rockable sealing members 561 and 552 respectively, are mounted on shafts 593 and 564 respectively. Said shafts extend through end wall 549 with bearing mountings as respects one end thereof, While the other end has a closed end bearing in wall 548. On shafts 553 and 554 are mounted lever arms 555 and 559 respectively, the outer ends of which are operatively connected to a joining rod 551, Fig. 13. On this rod 551 is mounted resilient member 559 which bears against the outer end portion of lever arm 555, through which said rod slidingly passes in hole 559. This construction corresponds to interconnecting means for partitioning members 544 and 555. On shaft 54! is preferably mounted flywheel 519.

Trapped liquid chambers 5' and 512 are formed between abutment members 559 and 559, partitioning members 544 and 545 and ring 543. Openings 513 and 514 in chambers 51! and 512 respectively are joined by tube 515 for establishing hydraulic interconnecting means as previously described for other forms of my invention.

Compartments 551 and 558 are provided respectively with working or expansion cylinders 515 and 511, having fuel injectors 518 and 519. In cylinders 516. and 51'. are exhaust valve seats 585 and 531 and modified sleeve valves 582 and 18 583, in the upper end of which are exhaust ports 584 and 585 respectively with seats 586 and 581 at the top. At the bottom, said sleeve valves have inwardly projecting rings 588 and 589 (as shown threadedly mounted to permit assembly). Beneath said rings are flexible annular sealing members 590 and 59L Stops 592 and 593 are mounted on the housing 549 to provide a lower limit of travel for the sleeve valves 582 and 583.

In sleeve valves 582 and 583 are pistons 594 and 595 which have tubular piston rods 595 and 591 extending downwardly through compartments 551 and 555 into double acting air compressing cylinders 598 and 599 respectively through packing 555 and 691. In pistons 594 and 555 are poppet valves 60?. and 603 respectively which are seatingly mounted in tubes 596 and 591. Poppet valve 683 with stem 694 is slidingly guided in a spider 605. Spring 686 is mounted on said stem 594. Poppet valve 692 is identically mounted in tube 595 but is not shown in the interest of brevity.

On the lower end of tubes 599 and 591, Fig. 12, are mounted air compressing pistons 591 and 598. In upper part of cylinders 598 and 599 are recessed air by-pass ports 599 and 519 respectively. Upper parts of cylinders 598 and 599 communicate with chambers 6H and 5I2 respectively having conventional spring loaded air intake valves 513 and 514 with seats 515 and 815 in wall 511 of air intake chamber 618. The bottom part of cylinders 598 and 599 communicates with air chambers 519 and 628 respectively, having conventional spring loaded air intake valves 621 and 522 with seats B23 and 624 respectively in wall 525 of air intake chamber 618.

On piston rod tubes 595 and 591, Fig. 1-2, are collars 525, 621, 628, and 529 respectively engageable with slidable members 539 and 531 having ports 532 and 6-39 registerable with ports 534 and 535 in pressure relief and liquid make-up boxes 936 and 631. Since these boxes are of identical construction only box 631 will be described in detail. Port 535 opens into chamber 638 communieating with chamber 639 in which is spring loaded relief valve 649. Chamber 639 communicates through opening 641 with reservoir 542. Chamber 938 has spring loaded suction valve 543 gliough which liquid is drawn from reservoir The mode of operation of the modified form of my invention set forth above is as follows:

The general mode of operation of this form of my invention so far as the fundamentals are concerned is the same in general as that set forth herein for the other forms. Partition members 544 and 545 arcuately mounted are held in sealing tight engagement with ring 543 as follows: As said ring 543 follows the eccentric orbit of displacement member 542 there is directly imparted a primary reciprocal motion to partitioning members 544 and 545 and this in turn is imparted to lever arms 552 and 555 and simultaneously also a secondary motion is imparted to said partitioning members and arms du to change i their spaced relationship induced by the eccentric character of displacement member 542, That is, said partitioning members 544 and 545 may move in opposite directions and their lever arms 552 and 553 move in the same direction during different phases of the rotative cycl but always they are maintained in close sealing contact with respect to ring 543 due to the action of resilient means 555 on joining rod 554. Tube 515 provides for relieving the pressures in whichever chamber or 512 the liquid may be trapped by transferring the trapped liquid to that chamber having the lesser pressure. The above construction makes possible in a practical way the arouate movement of partitioning members 544 and 545 to effectively sealingly bear upon rotating displacement member 542 through ring 543.

Arcuately mounted abutment members 559 and 588 have identical mounting construction tying them in cooperative action and mode of operation as said partitioning members 544 and 545, so that their mode of operation will not be repeated in the interest of brevity.

As shown in Fig. 12, cylinder 516 has fired and piston 565 is at the bottom of its stroke whereby it has contacted and moved sleeve valve 582 downward opening the exhaust port 584 in the top from its seat 588 to allow exhaust gases under pressure due to expansion to escape through exhaust pipes 644 (cylinder 511 has exhaust pipe 655). After said first expulsion of exhaust gases and resulting drop in pressure within the expansion chamber of sleeve valve 582, valve 682 is opened by the air pressure within tubular piston rod 586. Thereupon there occurs inflow scavenging of the exhaust gases leaving undiluted air in said expansion chamber, which is now available for compression and the injection of fuel at the next explosion phase of the cycle.

Valve 602 will be forcibly closed due to its inertia and its spring, when piston 594 is forced upwardly by the liquid in compartment 551, when said liquid is displaced in compartment 551 by the rotation of displacement member 542. This liquid displacement forces flexible sealing ring 568 into sealing contact with ring 588 carried by sleeve valve 582, and moves said sleeve valve 582 with said flexible ring 588 and piston 594 upwardly until seat 586 of sleeve valve 582 seats against exhaust valve seat 588. Piston 594 then continues to move upwardly with intake valve 602 in tightly closed position and compression of the air in said sleeve valve 582 is compressed for the next cycle of fuel injection. The scavenging air under pressure in tubular piston rod 596, which, as stated above, opened valve 602, was supplied as follows: As piston 601 descended, air previously drawn in through valve 62! and which was augmented in volume by the previous upward air compression stroke which by-passed the piston from its upper side to its underside through bypass ports 689 when the piston uncovered its lower portion. During its continued downward stroke valve 6H3 opens by atmospheric pressure and air is admitted to chamber 6!! from air intake 6l8. When piston 601 reaches the bottom of its stroke, valve 6 i 8 is closed by its spring. When piston 601 started downwardly valve 62! was closed by its spring.

Piston 595 and its associated parts operates in opposite phase in the same manner as said piston 594 and hence its operation will not be further described.

Pressure relief and make-up box function as follows: Port 633 in slidable member 63! is in open register with port 635, being so positioned by the previous downward stroke of tubular piston rod 591 and its collar 628. When the liquid in compart 558 came under pressure due to the rotation of displacement member 542, said pressure was transmitted through ports 633 and 635 to liquid in chamber 638. When this pressure exceeds the set pressure of the spring loaded relief valve 640, the valve opens and the pressure is relieved by liquid passing into chamber 639,

thence through opening 64! into reservoir 642. As tubular piston rod 591 nears its upper limit of travel, collar 629 engages slidable member 63! and moves port 633 upwardly and out of registry with port 635. Thus, sealing off any further escape of liquid into reservoir 642 While the next expansion stroke takes place. As piston 595 nears the bottom of its stroke, collar 628 engages slidable member 63! forcing it downward until port 633 is again in registry with port 635. If at this time there is any deficiency of liquid in compartment 558 due to any leakage from said compartment 558, liquid from reservoir 642 is forced under atmospheric pressure through valve 643 into chamber 838, thence through ports 635 and 633 and into compartment 558. Valve 643 is then closed by its spring and the liquid in said compartment 558 is then ready for the next displacement by the rotation of displacement member 542.

In Fig. 15, a modified form of the tubular piston rod and scavenging air admission means of Fig. 12 is shown suitable for aspiration for Otto cycle operation or by timed fuel injection means, i. e., in this form there is not a fuel injector means at the top of the expansion cylinder corresponding to injection means 518 in Fig. 12, but there is substituted a conventional fuel ignition means, such as spark plug 655. Air intake valve 650, corresponding to air intake valve 602 in Fig. 12, is floatingly guided by spider bracket 65! mounted within tubular piston rod 652 which has mounted on its upper end portion piston 653 which in turn reciprocates within sleeve valve 654, which in turn reciprocates in cylinder 660. Tubular fuel conveying and air intake valve positive opening means 556 is fixedly mounted in an air compression cylinder head 651 and is connected to fuel supply line 658. Tube 656 is closed at its upper end which functions to open valve 650 as shown. Also at its upper end are laterally disposed jet holes 659 to permit fuel to enter scavenging air stream from air compressing cylinder 666 by suction induced by the flow of the scavenging air past the jet holes 659 after valve 650 has been opened and the first rush of undiluted air has started scavenging the exhaust gases. The first portion of undiluted scavenging air is followed by the air fuel mixture which rises in cylinder 660.

When the scavenging air has scavenged the exhaust gases, then the sleeve valve 654 is pushed upwardly by the power transmitting liquid member 66! so that valve seat 662 in sleeve valve 654 is sealingly engaged with registering seat 663. Thus, the scavening is accomplished with undiluted or pure air so that the fuel air mixture next following is conserved exclusively for combustion instead of being partly used for scavenging as in the conventional two-cycle engine. As said liquid 66! moves the sleeve valve 654 upwardly, piston 653 is likewise moved upwardly by the liquid 66! operating through opening 664 so as to bear against the underside portion of piston 653 which in its upward travel closes valve 650 floatingly mounted thereon.

Fuel mixture is admitted to fuel tube 658 and to its extension 656 by suction created by the rapid passage of scavenging air past ports 659 as above set forth from a carburization or a fuel atomizing mechanism 665 of standard common practice carburetor design.

Fig. 16 illustrates a second modified form of the mechanism illustrated in Fig. 12 as respects valving of the working cylinder which does not employ the sleeve type valve as in Figs. 12 and 15-poppet type exhaust valves 615 being substituted therefor. In poppet type exhaust valves 615, the valve stems 616 are floatingly mounted in piston an which carries valve stem cylinders 678 in sealed relation against the power transmitting liquid member 619. Piston 611 is slidingly mounted in working cylinder 580 having a water cooling jacket t8]. Stems 61B are provided with resilient means 682 which act to close valves 615 when not being held open by the downward travel of piston fill.

Intake valve 683 is floatingly mounted within piston tubular member 684 which in turn has mounted therein a valve opening rod 685 which is fixedly secured to lower cylinder head 586. Fuel is admitted through fuel injector nozzle 681.

Expansion of gases in cylinder 680 forces piston it'll downward, thereby opening poppet valves 875 by engaging collars 688 mounted on valve stems E575 at the lower portion of travel of the piston (ill. The downward travel of piston 51-! also causes engagement of stem 683a of valve 683 mounted thereon with rod 685, thereby opening same and admitting scavenging air from tubular member 6%. This scavenging air supply is similarly provided for as in Fig. 12 by pistons 60'! and 688.

As the scavenging of the cylinder 58!] is completed, the piston fill is moved upwardly by liquid member 619 and in so doing poppet valves 615 are closed by resilient means 682 against exhaust valve seats 689. Intake air valve 683 is closed by its inertia as piston Ell moves upwardly against it. Valve stem cylinders 618 obviously function as valve stem Sill receiving means.

The mode of operation of the inventions herein described has been set forth in conjunction with the structural descriptions in order to render the same more clear and readily understood.

I claim:

1. A device of the character described comprising a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; a periodically occurring force-developing fluid in said working chamber; power transmitting liquid forming a reciprocating liquid piston-like body in said working chamber; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; movable partitioning members located above and below said displacement member, each of which members contact said displacement member, each of which members contacts said displacement member in substantially a vertical plane through said shaft, thereby, in conjunction with said displacement member, dividing said liquid chamber into a plurality of compartments; and two abutment members arcuately movably mounted in said compartments, one having one end pivotally mounted in the upper wall of said liquid compartment and the other member having one end pivotally mounted in the lower wall of said compartment, the other end of said members contacting said displacement member in a plane extending substantially horizontally through said shaft whereby the pressure of said power transmitting liquid is applied to a selected segment of said displacement member as respects each compartment, that is, when the leverage arm of said displacement member is greatest in that compartment.

2. In a device of the character described, a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; power transmitting liquid forming a liquid piston-like body in said working cylinder; a periodically occurring force-developing fluid in said working cylinder; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; a piston mounted in said working chamber having a poppet valve; an air compression means; and a tubular piston means connecting said piston and said air compression means, said tubular piston extending through said power transmitting liquid whereby compressed air periodically passed through said tubular piston scavenges spent gases in said working cylinder and cools said power transmitting liquid.

3. A device of the character described comprising a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; power transmitting liquid forming a reciprocating liquid pistondike body in said Working chamber; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; movable partitioning members mounted on said housing of said liquid chamber on opposite sides of said displacement member, each partitioning member contacting said displacement member on opposite sides thereof substantially in a plane through the axis of said shaft, thereby, in conjunction with said displacement member, dividing said liquid chamber into a plurality or" compartments, and a movable abutment member disposed in each of said compartments resiliently held against said displacement mem-- her as to one end portion in contacting said displacement member in a plane extending substantially through said shaft and forming one side of said compartment otherwise bounded by said partition member and said displacement member, from which compartment a pressure developed in said power transmitting liquid is substantially excluded whereby the pressure of said power transmitting liquid is applied to a selected segment of said displacement member as respects each compartment, that is, when the leverage arm of said displacement member is greatest in that compartment.

4. A device of the character describe-d comprising a housing forming a liquid chamber; a power transmitting liquid in said chamber; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; movable partitioning means mounted on said housing of said liquid chamber on opposite sides of said displacement member, each partitioning member contacting said displacement member on opposite sides thereof substantially in a plane through the axis of said shaft thereby, in conjunction with said displacement member, dividing said liquid chamber into a plurality of compartments; an abutment member disposed in each of said compartments extending as a yielding wall between the housing and the displacement member limiting and directing the periodically developed pressure of said power transmitting liquid in each compartment substantially to predetermined segments of said displacement member whereby the pressure is applied to the displacement member during the period when said displacement member presents its greatest leverage arm in that compartment; a changeable volume trapped liquid chamber bounded by said displacement member. abutment member and partitioning member in 253 each compartment; and a conduit interconnecting said trapped chambers whereby the pressure developed in one trapped chamber may be released in the other.

5. A device of the character described comprising a housing forming a liquid chamber; a power transmitting liquid in said chamber; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power trans mitting liquid may be reciprocated; a movable partitioning means mounted on said housing of said liquid chamber and extending to said displacement member thereby dividing said chamber into a plurality of substantially equal compartments; an abutment means disposed in each of said compartments extending as a yielding wall between the housing and the displacement member limiting and directing the periodically developed pressure of said power transmitting liquid in each compartment substantially to predetermined segments of said dipslacement member, whereby the pressure is applied to the displacement member during the period when it presents its greatest leverage arm in that compartment; and rockable concave faced blocks sealingly and suriace-bearingly contacting the displacement member, said blocks being carried by said partitioning and abutment members.

6. A device of the character described comprising, a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; power transmitting liquid in said chamber forming a reciprocating liquid body in said working cylinder; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; a movable partitioning member mounted on said housing of said liquid chamber, thereby, in conjunction with said displacement member, dividing said chamber into a plurality of compartments; and an abutment member disposed in each of said compartments extending as a yielding wall between the housing and the displacement member limiting and directing the periodically developed pressure of said power transmitting liquid in each compartment substantially to predetermined segments of said displacement member whereby the pressure of said liquid is applied to the displacement member during the period when it presents its greatest leverage arm in that compartment.

7. In a device of the character described comprising, a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; power transmitting liquid forming a reciprocating liquid body in said chamber; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; movable partitioning members mounted on said housing of said liquid chamber on opposite sides of said displacement member, each partitioning member contacting said displacement member on opposite sides thereof substantially in a plane through the axis of said shaft and, in conjunction with said displacement member, dividing said liquid chamber into a plurality of compartments; and an abutment member in each compartment movably mounted on said housing of said liquid chamber located on opposite sides of said displacement member and contacting said displacement member on opposite sides substantially in a plane through the axis of said shaft, which plane is normal to said first-mentioned plane whereby the pressure of said power transmitting liquid is periodically applied to a selected segment of said displacement member as the same is presented in each compartment in employing the greatest leverage of said displacement member.

8. In a device of the character described, a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; a power transmitting liquid in said chamber forming a reciprocating liquid body in said working cylinder; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; a partitioning member mounted on the housing as to one end portion thereof and extending to and contacting said displacement member in dividing said liquid chamber into a plurality of compartments; and an abutment member disposed in each of said compartments having one end portion thereof in contacting relation with the displacement member at a point substantially midway between said partitioning members, said abutment member limiting and directing the periodically developed pressure of said power transmitting liquid in each compartment substantially to predetermined segments of said displacement member whereby the pressure of said liquid is applied to the displacement member during the period when it presents its greatest leverage arm in that compartment.

9. In a device of the character described, a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; a valve seat mounted in said working cylinder; a power transmitting liquid in said liquid chamber forming a reciprocating liquid body in said working cylinder; a slidable sleeve valve having an exhaust port valve seat in the top thereof registerable with said seat first-named, in each of said working cylinders, and a piston with a poppet valve reciprocally disposed within said sleeve valve, said sleeve valve being hydraulically lifted into closed position with respect to its exhaust port valve seat by said power transmitting liquid; a tubular piston rod connected to said piston in said working chamber and communicatively connected to said compressed air developing means, said tubular piston rod extending through said power transmitting liquid and functioning as a heat transfer means in cooling said power transmitting liquid; an eccentrically mounted rotatable displacement member mounted on said shaft whereby said power transmitting liquid may be reciprocated; a movable partitioning member mounted on said housing of said liquid chamber on opposite sides of said displacement member, each partitioning member contacting said displacement member on opposite sides thereof substantially in a plane through the axis of said shaft, thereby, in conjunction with said displacement member, dividing said liquid chamber into a plurality of compartments; and an abutment member movably mounted on said housing of said liquid chamber on opposite sides of said displacement member and contacting said displacement member on opposite sides substantially midway between the partitioning contacts with the displacement member whereby force is periodically applied to a selected segment of said displacement member in each compartment in employing its greatest leverage.

10. A device of the character described, comprising a housing forming a liquid chamber; a shaft extending through said liquid chamber; a working cylinder connected to said liquid chamber; power transmitting liquid forming a reciprocating body in said working cylinder; an eccentrically mounted rotatable member mounted on said shaft whereby said power transmitting liquid may be reciprocated; a movable partitioning member mounted on said housing of said liquid chamber on opposite sides of said displacement member, each partitioning member contacting said displacement member on opposite sides thereof substantially in a plane through the axis of said shaft; thereby, in conjunction with said displacement member, dividing said liquid chamber into a plurality of compartments; an abutment member disposed in each of said compartments, having one end portion thereof in contacting relation with the displacement member at a point substantially midway between said partitioning members, said abutment member limiting and directing the periodically developed pressure of said power transmitting liquid in each compartment substantially to predetermined segments of said displacement member, whereby the pressure of said liquid is applied to the displacement member during the period when it presents its greatest leverage arm in that compartment; and a resilient mechanically interconnecting means joining said abutment members whereby displacement of one abutment member by said displacement member actuates the other into sealing position and whereby compensation is provided for the differences in movement of said abutment members.

HAL DE WAIDE.

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